JP2009133266A - Waste heat utilization device for internal combustion engine - Google Patents

Waste heat utilization device for internal combustion engine Download PDF

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JP2009133266A
JP2009133266A JP2007310501A JP2007310501A JP2009133266A JP 2009133266 A JP2009133266 A JP 2009133266A JP 2007310501 A JP2007310501 A JP 2007310501A JP 2007310501 A JP2007310501 A JP 2007310501A JP 2009133266 A JP2009133266 A JP 2009133266A
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working fluid
temperature
regenerator
expander
evaporator
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Junichiro Kasuya
潤一郎 粕谷
Yasuaki Kano
靖明 狩野
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Sanden Corp
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Sanden Corp
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

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Abstract

<P>PROBLEM TO BE SOLVED: To provide a waste heat utilization device for internal combustion engine, whose energy recovery efficiency can be surely improved by precisely controlling a heating amount of a working fluid. <P>SOLUTION: A Rankne cycle (8) includes a first regenerator (32) which heats a working fluid inflowing to an evaporator (10) by using a working fluid allowed to outflow from an expander (20) and a second regenerator (34) which heats a working fluid allowed to outflow from the evaporator by using the working fluid allowed to outflow from the expander. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、内燃機関の廃熱利用装置に係り、詳しくは、車両に用いられて好適な内燃機関の廃熱利用装置に関する。   The present invention relates to a waste heat utilization device for an internal combustion engine, and more particularly to a waste heat utilization device for an internal combustion engine suitable for use in a vehicle.

この種の内燃機関の廃熱利用装置は、例えばエンジンが搭載された車両に適用され、エンジンの廃熱により冷媒を加熱する蒸発器、該蒸発器から流出された冷媒を膨張させて駆動力を発生する膨張機、該膨張機から流出された作動流体を凝縮させる凝縮器を有し、該凝縮器から流出された作動流体が前記蒸発器に流入されて循環するランキンサイクルを備え、エンジンの廃熱からエネルギーを回収している。   This type of waste heat utilization device for an internal combustion engine is applied to, for example, a vehicle equipped with an engine. An expander that is generated, a condenser that condenses the working fluid that has flowed out of the expander, and a Rankine cycle in which the working fluid that has flowed out of the condenser flows into the evaporator and circulates, It recovers energy from heat.

そして、膨張機と凝縮器との間に、膨張機から流出された冷媒にて蒸発器に流入される冷媒を加熱する冷媒の再生器を設けたランキンサイクルが知られている（例えば、特許文献１参照）。
特開昭５９−４１６０９号公報 And the Rankine cycle which provided the regenerator of the refrigerant | coolant which heats the refrigerant | coolant which flows in into an evaporator with the refrigerant | coolant which flowed out from the expander between the expander and a condenser is known (for example, patent document) 1).
JP 59-41609

しかしながら、上記従来技術では、膨張機から流出された冷媒の温度が蒸発器から流出された冷媒の温度よりも高くなる場合があり、再生器にて単に蒸発器に流入される冷媒を加熱するのみでは、膨張機から流出された冷媒の熱を最大限に利用していないとの問題がある。
本発明は、このような課題に鑑みてなされたもので、膨張機から流出された冷媒の熱を最大限に利用することにより、エネルギー回収効率を確実に向上することができる内燃機関の廃熱利用装置を提供することを目的とする。 However, in the above prior art, the temperature of the refrigerant flowing out of the expander may be higher than the temperature of the refrigerant flowing out of the evaporator, and the regenerator simply heats the refrigerant flowing into the evaporator. However, there is a problem that the heat of the refrigerant that has flowed out of the expander is not utilized to the maximum extent.
The present invention has been made in view of such a problem, and waste heat of an internal combustion engine that can reliably improve energy recovery efficiency by making maximum use of the heat of the refrigerant that has flowed out of the expander. It aims at providing a utilization apparatus.

上記の目的を達成するべく、請求項１記載の内燃機関の廃熱利用装置は、内燃機関の廃熱により作動流体を加熱する蒸発器、該蒸発器から流出された作動流体を膨張させて駆動力を発生する膨張機、該膨張機から流出された作動流体を凝縮させる凝縮器を有し、該凝縮器から流出された作動流体が蒸発器に流入されて循環するランキンサイクルを備え、ランキンサイクルは、膨張機から流出された作動流体にて蒸発器に流入する作動流体を加熱する第１再生器と、膨張機から流出された作動流体にて蒸発器から流出する作動流体を加熱する第２再生器とを有することを特徴としている。   In order to achieve the above object, a waste heat utilization apparatus for an internal combustion engine according to claim 1 is driven by an evaporator that heats the working fluid by the waste heat of the internal combustion engine, and the working fluid that has flowed out of the evaporator is expanded. An expander that generates force, a condenser that condenses the working fluid that has flowed out of the expander, and a Rankine cycle in which the working fluid that has flowed out of the condenser flows into the evaporator and circulates, The first regenerator that heats the working fluid that flows into the evaporator with the working fluid that has flowed out of the expander, and the second that heats the working fluid that flows out of the evaporator with the working fluid that has flowed out of the expander And a regenerator.

また、請求項２記載の発明では、請求項１において、ランキンサイクルは、第２再生器をバイパスするバイパス路と、膨張機から流出された作動流体をバイパス路と第２再生器とに配分して流入させる流量配分制御手段とを有することを特徴としている。
更に、請求項３記載の発明では、請求項２において、流量配分制御手段は、膨張機に流入される作動流体の温度を検出する第１温度検出手段と、膨張機から第２再生器に流入される作動流体の温度を検出する第２温度検出手段と、蒸発器から第２再生器に流入される作動流体の温度を検出する第３温度検出手段と、第１〜第３温度検出手段にて検出された作動流体の温度に基づいて、第２再生器側またはバイパス路側を連通させるべく開駆動される操作端とからなることを特徴としている。 According to a second aspect of the present invention, in the first aspect, the Rankine cycle distributes the working fluid flowing out from the bypass passage and the second regenerator to the bypass passage and the second regenerator. And a flow rate distribution control means for inflow.
Further, according to a third aspect of the present invention, in the second aspect, the flow rate distribution control means includes a first temperature detecting means for detecting the temperature of the working fluid flowing into the expander, and an inflow from the expander to the second regenerator. Second temperature detecting means for detecting the temperature of the working fluid, third temperature detecting means for detecting the temperature of the working fluid flowing into the second regenerator from the evaporator, and first to third temperature detecting means And an operating end that is driven to open to communicate with the second regenerator side or the bypass path side based on the detected temperature of the working fluid.

更にまた、請求項４記載の発明では、請求項３において、流量配分制御手段は、第２温度検出手段にて検出された作動流体の温度が第３温度検出手段にて検出された温度以下となるとき、操作端をバイパス路側に全開させることを特徴としている。
また、請求項５記載の発明では、請求項４において、流量配分制御手段は、第１温度検出手段にて検出された作動流体の温度が所定の設定温度より大きくなるとき、操作端をバイパス路側に開駆動させ、第１温度検出手段にて検出された作動流体の温度が所定の設定温度以下となるとき、操作端を第２再生器側に開駆動させることを特徴としている。 Furthermore, in the invention described in claim 4, in claim 3, the flow rate distribution control means is configured such that the temperature of the working fluid detected by the second temperature detection means is equal to or lower than the temperature detected by the third temperature detection means. In this case, the operation end is fully opened to the bypass path side.
According to a fifth aspect of the present invention, in the fourth aspect, when the temperature of the working fluid detected by the first temperature detecting means is greater than a predetermined set temperature, the flow rate distribution control means sets the operating end to the bypass path side. And when the temperature of the working fluid detected by the first temperature detecting means is equal to or lower than a predetermined set temperature, the operating end is driven to open toward the second regenerator.

更に、請求項６記載の発明では、請求項５において、所定の設定温度は、作動流体の分解温度未満の最大値をなすことを特徴としている。
更にまた、請求項７記載の発明では、請求項１乃至６の何れかにおいて、ランキンサイクルは、蒸発器を経て第２再生器から流出された作動流体を内燃機関の排ガスにて加熱する加熱器を有することを特徴としている。 Furthermore, the invention described in claim 6 is characterized in that, in claim 5, the predetermined set temperature has a maximum value lower than the decomposition temperature of the working fluid.
Furthermore, in the invention according to claim 7, in any one of claims 1 to 6, the Rankine cycle is a heater for heating the working fluid discharged from the second regenerator through the evaporator with the exhaust gas of the internal combustion engine. It is characterized by having.

また、請求項８記載の発明では、請求項３乃至７の何れかにおいて、操作端は、第１〜第３温度検出手段にて検出された作動流体の温度に応じて該操作端の作動位置が連続的に可変駆動されるリニア三方弁であることを特徴としている。   According to an eighth aspect of the present invention, in any one of the third to seventh aspects, the operating end is an operating position of the operating end according to the temperature of the working fluid detected by the first to third temperature detecting means. Is a linear three-way valve that is continuously variably driven.

請求項１記載の本発明の内燃機関の廃熱利用装置によれば、ランキンサイクルが膨張機出口の作動流体にて蒸発器入口、蒸発器出口の作動流体をそれぞれ加熱する第１、第２再生器を有することにより、凝縮器の熱負荷は不変のままで、膨張機入口における作動流体の加熱量、ひいてはランキンサイクルにおける回収エネルギーを増大することができるため、廃熱利用装置のエネルギー回収効率を向上することができる。   According to the waste heat utilization apparatus for an internal combustion engine of the present invention, the Rankine cycle heats the working fluid at the evaporator inlet and the evaporator outlet with the working fluid at the expander outlet, respectively. Since the heat load of the condenser remains unchanged, the heating amount of the working fluid at the inlet of the expander, and thus the recovered energy in the Rankine cycle can be increased, so that the energy recovery efficiency of the waste heat utilization device can be increased. Can be improved.

また、請求項２記載の発明によれば、ランキンサイクルが膨張機から流出した作動流体を第２再生器のバイパス路と第２再生器とに配分して流入させる流量配分制御手段を有することにより、内燃機関やランキンサイクルの作動状況に応じて膨張機入口における作動流体の加熱量を適正に制御することができるため、廃熱利用装置のエネルギー回収効率を更に効果的に向上することができる。   According to the second aspect of the present invention, the Rankine cycle has flow rate distribution control means for distributing and flowing the working fluid flowing out of the expander to the bypass path of the second regenerator and the second regenerator. Since the heating amount of the working fluid at the inlet of the expander can be appropriately controlled according to the operating conditions of the internal combustion engine and Rankine cycle, the energy recovery efficiency of the waste heat utilization device can be further effectively improved.

具体的には、請求項３記載の発明によれば、流量配分制御手段は、膨張機入口の作動流体の温度を検出する第１温度検出手段と、膨張機から第２再生器に流入される作動流体の温度を検出する第２温度検出手段と、蒸発器から第２再生器に流入される作動流体の温度を検出する第３温度検出手段と、これら第１〜第３温度検出手段にて検出された作動流体の温度に基づいて、第２再生器側またはバイパス路側を連通させるべく開駆動される操作端とから構成されている。   Specifically, according to the third aspect of the present invention, the flow rate distribution control means flows into the second regenerator from the first temperature detection means for detecting the temperature of the working fluid at the inlet of the expander. The second temperature detecting means for detecting the temperature of the working fluid, the third temperature detecting means for detecting the temperature of the working fluid flowing into the second regenerator from the evaporator, and the first to third temperature detecting means Based on the detected temperature of the working fluid, the operation end is driven to open to communicate the second regenerator side or the bypass path side.

このような流量配分制御手段の構成において、請求項４記載の発明によれば、第２温度検出手段にて検出された作動流体の温度が第３温度検出手段にて検出された温度以下となるとき、操作端をバイパス路側に全開させる。これにより、内燃機関のアイドリング時などにその廃熱が少なくなって蒸発器出口の作動流体で膨張機出口の作動流体を加熱するといった熱交換の逆転現象を防止することができる。従って、膨張機入口における作動流体の温度低下や凝縮を確実に防止できるため、ランキンサイクルを適正に稼働しつつ、廃熱利用装置のエネルギー回収効率を確実に向上することができる。   According to the fourth aspect of the present invention, the temperature of the working fluid detected by the second temperature detecting means is equal to or lower than the temperature detected by the third temperature detecting means. When the operation end is fully opened to the bypass path side. As a result, it is possible to prevent the reverse phenomenon of heat exchange such that the waste heat is reduced when the internal combustion engine is idling and the working fluid at the evaporator outlet is heated by the working fluid at the evaporator outlet. Therefore, since the temperature drop and condensation of the working fluid at the inlet of the expander can be reliably prevented, it is possible to reliably improve the energy recovery efficiency of the waste heat utilization device while properly operating the Rankine cycle.

上記制御に加え、請求項５記載の発明によれば、流量配分制御手段は、第１温度検出手段にて検出された作動流体の温度が所定の設定温度より大きくなるとき、操作端をバイパス路側に開駆動させ、第１温度検出手段にて検出された作動流体の温度が所定の設定温度以下となるとき、操作端を第２再生器側に開駆動させる。これにより、作動流体の加熱量の増大に伴って作動流体の温度が極端に高温になることを防止することができる。   According to the invention described in claim 5, in addition to the above control, the flow rate distribution control means sets the operation end to the bypass path side when the temperature of the working fluid detected by the first temperature detection means is higher than a predetermined set temperature. When the temperature of the working fluid detected by the first temperature detecting means is equal to or lower than a predetermined set temperature, the operating end is opened to the second regenerator side. Thereby, it can prevent that the temperature of a working fluid becomes extremely high with the increase in the heating amount of a working fluid.

具体的には、請求項６記載の発明によれば、所定の設定温度を作動流体の分解温度未満の最大値とすることにより、作動流体の劣化や作動流体に添加される潤滑油の分解を防止しつつ、作動流体の加熱量を増大させることができるため、ランキンサイクルを適正に稼働しつつ、廃熱利用装置のエネルギー回収効率を更に確実に向上することができる。
また、請求項７記載の発明によれば、ランキンサイクルが蒸発器を経て第２再生器から流出された作動流体を内燃機関の排ガスにて加熱する加熱器を有することにより、膨張機入口の作動流体の加熱量、ひいてはランキンサイクルにおける回収エネルギーを更に増大することができ、廃熱利用装置のエネルギー回収効率をより一層向上することができる。 Specifically, according to the sixth aspect of the invention, the predetermined set temperature is set to a maximum value lower than the decomposition temperature of the working fluid, so that the working fluid is deteriorated or the lubricating oil added to the working fluid is decomposed. Since the amount of heating of the working fluid can be increased while preventing, the energy recovery efficiency of the waste heat utilization apparatus can be improved more reliably while operating the Rankine cycle properly.
According to the seventh aspect of the present invention, the Rankine cycle includes the heater that heats the working fluid that has flowed out of the second regenerator through the evaporator with the exhaust gas of the internal combustion engine. The heating amount of the fluid, and hence the recovery energy in the Rankine cycle can be further increased, and the energy recovery efficiency of the waste heat utilization apparatus can be further improved.

更に、請求項８記載の発明によれば、操作端が第１〜第３温度検出手段にて検出された作動流体の温度に応じて該操作端の作動位置が連続的に可変駆動されるリニア三方弁であることにより、膨張機を経由した作動流体を作動流体の全流量域に亘って第２再生器のバイパス路と第２再生器とに配分して流入させることができる。これにより、流量配分制御手段の制御性を向上することができるため、廃熱利用装置のエネルギー回収効率をより一層確実に向上することができる。   According to the eighth aspect of the present invention, the operating position of the operating end is continuously variably driven according to the temperature of the working fluid detected by the first to third temperature detecting means. By being a three-way valve, the working fluid passing through the expander can be distributed and fed to the bypass path of the second regenerator and the second regenerator over the entire flow rate range of the working fluid. Thereby, since the controllability of the flow rate distribution control means can be improved, the energy recovery efficiency of the waste heat utilization apparatus can be improved more reliably.

以下、図面により本発明の一実施形態について説明する。
図１は、本実施形態の廃熱利用装置２の構成を概略的に示した模式図である。廃熱利用装置２は、例えば車両のエンジン（内燃機関）４を冷却する冷却水回路６と、エンジン４の廃熱を回収するランキンサイクル回路（ランキンサイクル）８（以下、ＲＣ回路という）とから構成されている。 Hereinafter, an embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a schematic diagram schematically showing the configuration of the waste heat utilization apparatus 2 of the present embodiment. The waste heat utilization apparatus 2 includes, for example, a cooling water circuit 6 that cools a vehicle engine (internal combustion engine) 4 and a Rankine cycle circuit (Rankine cycle) 8 (hereinafter referred to as an RC circuit) that collects waste heat of the engine 4. It is configured.

冷却水回路６は、エンジン４から延設される冷却水の循環路７に、冷却水の流れ方向から順に蒸発器１０、ラジエータ１２、サーモスタット１４、水ポンプ１６が介挿されて閉回路を構成している。
蒸発器１０は、冷却水回路６の冷却水とＲＣ回路８の冷媒とを熱交換することにより、エンジン４で加熱された冷却水、すなわち温水を熱媒体としてエンジン４の廃熱をＲＣ回路８側に吸熱させて回収している。一方、蒸発器１０を通過して冷媒に吸熱された冷却水は、エンジン４を冷却することにより再び加熱された温水となる。 The cooling water circuit 6 forms a closed circuit by inserting an evaporator 10, a radiator 12, a thermostat 14, and a water pump 16 into a cooling water circulation path 7 extending from the engine 4 in order from the flow direction of the cooling water. is doing.
The evaporator 10 exchanges heat between the cooling water of the cooling water circuit 6 and the refrigerant of the RC circuit 8, thereby using the cooling water heated by the engine 4, that is, warm water as a heat medium, and the waste heat of the engine 4 as the RC circuit 8 It is collected by absorbing heat to the side. On the other hand, the cooling water that has passed through the evaporator 10 and is absorbed by the refrigerant becomes warm water that is heated again by cooling the engine 4.

ラジエータ１２は、蒸発器１０と直列に配列され、蒸発器１０を通過して冷媒に吸熱された冷却水を外気との熱交換により更に冷却している。
サーモスタット１４は、冷却水温度に応じてラジエータ１２へ通水される冷却水量を制御する機械式の三方切換弁であって、２つ入口ポートと１つの出口ポートとを有している。２つの入口ポートには、ラジエータ１２から延設される流路７ａと、蒸発器１０とラジエータ１２との間の流路７ｂからラジエータ１２を迂回して接続されるバイパス路７ｃとがそれぞれ接続され、これにより、冷却水温度に応じてラジエータ１２へ通水される冷却水量が増減されてエンジン４の過熱が防止される。 The radiator 12 is arranged in series with the evaporator 10 and further cools the cooling water that has passed through the evaporator 10 and has been absorbed by the refrigerant by heat exchange with the outside air.
The thermostat 14 is a mechanical three-way switching valve that controls the amount of cooling water that is passed to the radiator 12 according to the cooling water temperature, and has two inlet ports and one outlet port. A flow path 7a extending from the radiator 12 and a bypass path 7c connected by bypassing the radiator 12 from the flow path 7b between the evaporator 10 and the radiator 12 are connected to the two inlet ports, respectively. As a result, the amount of cooling water passed to the radiator 12 is increased or decreased according to the cooling water temperature, and the engine 4 is prevented from overheating.

水ポンプ１６は、エンジン４に装着され、エンジン４の回転数に応じて駆動されて冷却水回路６に冷却水を好適に循環させる。
一方、ＲＣ回路８は、冷媒の循環路９に、冷媒の流れ方向から順に蒸発器１０、加熱器１８、膨張機２０、凝縮器２２、気液分離器２４、冷媒ポンプ２６が順に介挿されて閉回路を構成している。 The water pump 16 is attached to the engine 4 and is driven according to the rotational speed of the engine 4 to circulate the cooling water in the cooling water circuit 6 suitably.
On the other hand, the RC circuit 8 includes an evaporator 10, a heater 18, an expander 20, a condenser 22, a gas-liquid separator 24, and a refrigerant pump 26 inserted in this order from the refrigerant flow direction in the refrigerant circulation path 9. Closed circuit.

加熱器１８は、エンジン４の排ガス管２８を流れる排ガスで冷媒を加熱する排ガス熱交換器であって、蒸発器１０で加熱された冷媒が更に加熱される。
膨張機２０は、蒸発器１０で加熱されて過熱蒸気の状態となった冷媒を膨張させ、回転駆動力を発生する容積式の流体機器であって、膨張機２０には、発生した回転駆動力を電力変換して廃熱利用装置２の外部で利用可能とする発電機３０が機械的に連結されている。 The heater 18 is an exhaust gas heat exchanger that heats the refrigerant with the exhaust gas flowing through the exhaust gas pipe 28 of the engine 4, and the refrigerant heated by the evaporator 10 is further heated.
The expander 20 is a positive displacement fluid device that expands the refrigerant heated to the superheated steam state by the evaporator 10 and generates a rotational driving force. The expanding device 20 includes the generated rotational driving force. A power generator 30 that converts the power to be used outside the waste heat utilization apparatus 2 is mechanically connected.

凝縮器２２は、膨張機２０から流出される冷媒を外気と熱交換させて凝縮液化する空冷式の熱交換器である。
気液分離器２４は、凝縮器２２にて凝縮された冷媒を気液二層に分離するレシーバであり、ここで分離された液冷媒のみが冷媒ポンプ２６側に流出される。
冷媒ポンプ２６は、その駆動部に入力される信号に応じて駆動される電動ポンプであり、凝縮器２２で凝縮され、気液分離器２４で分離された液冷媒は冷媒ポンプ２６によって蒸発器１０側に圧送され、ＲＣ回路８を好適に循環する。 The condenser 22 is an air-cooled heat exchanger that heat-exchanges the refrigerant flowing out of the expander 20 with the outside air to condense and liquefy it.
The gas-liquid separator 24 is a receiver that separates the refrigerant condensed in the condenser 22 into gas-liquid two layers, and only the liquid refrigerant separated here flows out to the refrigerant pump 26 side.
The refrigerant pump 26 is an electric pump that is driven in accordance with a signal input to the driving unit thereof. The liquid refrigerant condensed by the condenser 22 and separated by the gas-liquid separator 24 is evaporated by the refrigerant pump 26. Is circulated through the RC circuit 8 suitably.

ここで、ＲＣ回路８には、膨張機２０と凝縮器２２との間に、膨張機２０出口の冷媒にて蒸発器１０入口、蒸発器１０出口の冷媒をそれぞれ加熱する第１、第２再生器３２，３４が設けられている。
第１、第２再生器３２，３４は、ＲＣ回路８内を循環する冷媒同士で熱交換が行われる内部熱交換器であって、膨張機２０出口側の熱量を膨張機２０入口側に積極的に供給することにより、ＲＣ回路８における回収エネルギーを増大させている。 Here, the RC circuit 8 includes first and second regenerations in which the refrigerant at the inlet of the evaporator 10 and the refrigerant at the outlet of the evaporator 10 are heated between the expander 20 and the condenser 22 by the refrigerant at the outlet of the expander 20, respectively. Containers 32 and 34 are provided.
The first and second regenerators 32 and 34 are internal heat exchangers in which heat is exchanged between refrigerants circulating in the RC circuit 8, and the amount of heat on the expander 20 outlet side is positively transferred to the expander 20 inlet side. Thus, the recovered energy in the RC circuit 8 is increased.

以下、図２に示されるモリエル線図を参照し、例えばＲ１３４ａを冷媒として使用した場合のＲＣ回路８の熱収支について説明する。
先ず、冷媒ポンプ２６から送出された液冷媒（Ａ：３５℃）は、第１再生器３２（Ａ→Ｂ）、蒸発器１０（Ｂ→Ｃ：８０℃）、第２再生器３４（Ｃ→Ｄ）、加熱器１８（Ｄ→Ｅ）にて段階的に加熱され、エンタルピｉが増加した過熱蒸気のガス冷媒（Ｅ：１５０℃）にされる。 Hereinafter, the heat balance of the RC circuit 8 when, for example, R134a is used as a refrigerant will be described with reference to the Mollier diagram shown in FIG.
First, the liquid refrigerant (A: 35 ° C.) sent from the refrigerant pump 26 is supplied to the first regenerator 32 (A → B), the evaporator 10 (B → C: 80 ° C.), and the second regenerator 34 (C → D) It is heated stepwise by the heater 18 (D → E), and is converted into a gas refrigerant (E: 150 ° C.) of superheated steam with increased enthalpy i.

次に、冷媒（Ｅ）は、膨張機２０にて膨張することにより減圧され、エンタルピｉも減少される（Ｅ→Ｆ：１１０℃）。そして、膨張機２０を通過した冷媒は、第２再生器３４（Ｆ→Ｇ）、第１再生器３２（Ｇ→Ｈ）にて段階的に吸熱され、これら吸熱量は点線矢印で示すように、蒸発器１０出口、蒸発器１０入口にそれぞれ供給され、上述した第２再生器３４（Ｃ→Ｄ）、第１再生器３２（Ａ→Ｂ）の加熱量に略等しい大きさとなっている。   Next, the refrigerant (E) is decompressed by being expanded by the expander 20, and the enthalpy i is also reduced (E → F: 110 ° C.). Then, the refrigerant that has passed through the expander 20 is absorbed in stages by the second regenerator 34 (F → G) and the first regenerator 32 (G → H), and the endothermic amounts are indicated by dotted arrows. These are supplied to the outlet of the evaporator 10 and the inlet of the evaporator 10, respectively, and have a size substantially equal to the heating amount of the second regenerator 34 (C → D) and the first regenerator 32 (A → B) described above.

そして、冷媒（Ｈ）は、凝縮器２２にてエンタルピｉが減少した冷媒（Ｉ）にされ、冷媒ポンプ２６により加圧されて冷媒（Ａ）になり、冷媒（Ａ）は再び第１再生器３２に流入して次の冷凍サイクルに入り、上記Ａ〜Ｉの順にサイクルが繰り返される。
このように、第１、第２再生器３２，３４を設けることにより、被加熱側である膨張機２０入口側の冷媒の加熱量がＡ→Ｂ、Ｃ→Ｄにおいて増大する一方、その加熱量の増大分だけ加熱側である膨張機２０出口側の冷媒の吸熱量、すなわち再生量がＦ→Ｇ、Ｇ→Ｈにて増大し、第１、第２再生器３２，３４は、少なくとも、このようなＲＣ回路８における内部熱交換が可能な熱容量を有している。 Then, the refrigerant (H) is changed to the refrigerant (I) in which the enthalpy i is reduced by the condenser 22 and is pressurized by the refrigerant pump 26 to become the refrigerant (A), and the refrigerant (A) is again the first regenerator. 32 enters the next refrigeration cycle, and the cycle is repeated in the order of A to I.
Thus, by providing the first and second regenerators 32 and 34, the heating amount of the refrigerant at the inlet side of the expander 20 that is the heated side increases in A → B and C → D, while the heating amount The amount of heat absorbed by the refrigerant on the outlet side of the expander 20 that is the heating side, that is, the regeneration amount increases by F → G, G → H, and the first and second regenerators 32 and 34 are at least The RC circuit 8 has a heat capacity that allows internal heat exchange.

また、Ｅ→Ｆにおける冷媒の膨張は、理論的には、図２中に示される等エントロピ線Ｌiに沿って行われ、膨張機２０の仕事量は膨張機２０の入口と出口との冷媒のエンタルピｉの差に比例している。更に、エンタルピ変化に対する等エントロピ線Ｌiの傾きは、図２中の右方向に向かう冷媒温度の上昇に伴い小さくなることから、第１、第２再生器３２，３４を設けることにより、冷媒の加熱量が増大し、ひいては膨張機２０の膨張仕事、すなわちＲＣ回路８における回収エネルギーを増大させることができる。   Further, the expansion of the refrigerant in E → F is theoretically performed along the isentropic line Li shown in FIG. 2, and the work of the expander 20 is the amount of refrigerant at the inlet and outlet of the expander 20. It is proportional to the difference in enthalpy i. Further, since the slope of the isentropic line Li with respect to the change in enthalpy decreases as the refrigerant temperature rises in the right direction in FIG. 2, the first and second regenerators 32 and 34 are provided to heat the refrigerant. The amount can be increased, and the expansion work of the expander 20, that is, the recovered energy in the RC circuit 8 can be increased.

一方、膨張機２０出口と第２再生器３４入口との間には、リニア三方弁（操作端）３６が設けられている。三方弁３６は、１つの入口ポートと２つの出口ポートとを有する電動切換弁であって、２つの出口ポートには、第２再生器３４から延設される流路９ａと、第２再生器３４を迂回するバイパス路９ｂとがそれぞれ接続されている。そして、三方弁３６は、その駆動部に入力される入力信号に比例して１つの弁体を連続的に可変駆動することにより、入口ポートに流入する冷媒を各出口ポートからリニアに配分して流出させると共に、これら各配分流量を微調整可能に構成されている。   On the other hand, a linear three-way valve (operation end) 36 is provided between the expander 20 outlet and the second regenerator 34 inlet. The three-way valve 36 is an electric switching valve having one inlet port and two outlet ports. The two outlet ports include a flow path 9a extending from the second regenerator 34, and a second regenerator. A bypass path 9b that bypasses 34 is connected to each other. The three-way valve 36 linearly distributes the refrigerant flowing into the inlet port from each outlet port by continuously driving one valve body in a variable manner in proportion to the input signal input to the drive unit. It is configured to allow the flow rate to flow out and to finely adjust each of the distribution flow rates.

また、加熱器１８出口と膨張機２０入口との間には、膨張機２０入口の冷媒の温度Ｔ１を検出する第１温度センサ（第１温度検出手段）３８、膨張機２０出口と三方弁３６との間には、膨張機２０から第２再生器３４側に流入する冷媒の温度Ｔ２を検出する第２温度センサ（第２温度検出手段）４０、蒸発器１０出口と第２再生器３４入口との間には、蒸発器１０から第２再生器３４に流入する冷媒の温度Ｔ３を検出する第３温度センサ（第３温度検出手段）４２が設置されている。   Between the outlet of the heater 18 and the inlet of the expander 20, a first temperature sensor (first temperature detection means) 38 that detects the refrigerant temperature T 1 at the inlet of the expander 20, the outlet of the expander 20 and the three-way valve 36. Between the second expander 20 and the second regenerator 34, a second temperature sensor (second temperature detecting means) 40 for detecting the temperature T2 of the refrigerant, the evaporator 10 outlet, and the second regenerator 34 inlet. Is provided with a third temperature sensor (third temperature detecting means) 42 for detecting the temperature T3 of the refrigerant flowing from the evaporator 10 into the second regenerator 34.

これら第１〜第３温度センサ３８，４０，４２は、三方弁３６と共に車両及び廃熱利用装置２の総合的な制御を行う電子コントロールユニット（ＥＣＵ）４４に電気的に接続されており、ＥＣＵ４４は、第１〜第３温度センサ３８，４０，４２にて検出された冷媒温度Ｔ１，Ｔ２，Ｔ３に基づいて三方弁３６の弁体を駆動することによって第２再生器３４側またはバイパス路９ｂ側を連通させる三方弁開度制御を行っている（流量配分制御手段）。   These first to third temperature sensors 38, 40, 42 are electrically connected to an electronic control unit (ECU) 44 that performs comprehensive control of the vehicle and the waste heat utilization device 2 together with the three-way valve 36. The second regenerator 34 side or the bypass 9b is driven by driving the valve body of the three-way valve 36 based on the refrigerant temperatures T1, T2, T3 detected by the first to third temperature sensors 38, 40, 42. The three-way valve opening degree control for communicating the sides is performed (flow rate distribution control means).

以下、図３に示されるフローチャートを参照して、この三方弁開度制御について詳しく説明する。
先ず、三方弁開度制御が開始されると、Ｓ１（以下、Ｓはステップを表す）に移行する。
Ｓ１では、第２温度センサ４０にて検出された冷媒温度Ｔ２が第３温度センサ４２にて検出された冷媒温度Ｔ３より大きいか否かを判別する。判別結果が真（Ｙｅｓ）でＴ２＞Ｔ３が成立すると判定された場合にはＳ２に移行し、判別結果が偽（Ｎｏ）でＴ２＞Ｔ３が成立しないと判定された場合にはＳ３に移行する。 Hereinafter, the three-way valve opening degree control will be described in detail with reference to the flowchart shown in FIG.
First, when the three-way valve opening degree control is started, the process proceeds to S1 (hereinafter, S represents a step).
In S <b> 1, it is determined whether or not the refrigerant temperature T <b> 2 detected by the second temperature sensor 40 is higher than the refrigerant temperature T <b> 3 detected by the third temperature sensor 42. If it is determined that T2> T3 is established when the determination result is true (Yes), the process proceeds to S2. If it is determined that T2> T3 is not satisfied because the determination result is false (No), the process proceeds to S3. .

Ｓ２に移行した場合には、第１温度センサ３８にて検出された冷媒温度Ｔ１が１５０℃より大きいか否かを判別する。判別結果が真（Ｙｅｓ）でＴ１＞１５０℃が成立すると判定された場合にはＳ４に移行し、判別結果が偽（Ｎｏ）でＴ１＞１５０℃が成立しないと判定された場合にはＳ５に移行する。なお、ＲＣ回路８を循環するＲ１３４ａ冷媒やこの冷媒に添加される潤滑油の劣化・分解が確実に起こらない温度は約１５０℃である。   When the process proceeds to S2, it is determined whether or not the refrigerant temperature T1 detected by the first temperature sensor 38 is higher than 150 ° C. If it is determined that T1> 150 ° C. is established when the determination result is true (Yes), the process proceeds to S4. If it is determined that T1> 150 ° C. is not satisfied because the determination result is false (No), the process proceeds to S5. Transition. The temperature at which the R134a refrigerant circulating in the RC circuit 8 and the lubricating oil added to the refrigerant do not reliably deteriorate or decompose is about 150 ° C.

Ｓ１からＳ３に移行した場合には、三方弁３６をバイパス路９ｂ側に強制的に全開にして本制御ルーチンをリターンする。
一方、Ｓ２からＳ４に移行した場合には、三方弁３６をバイパス路９ｂ側に開駆動して本制御ルーチンをリターンする。
これに対し、Ｓ２からＳ５に移行した場合には、三方弁３６を第２再生器３４側に開駆動して本制御ルーチンをリターンする。 In the case of shifting from S1 to S3, the three-way valve 36 is forcibly fully opened to the bypass path 9b side, and this control routine is returned.
On the other hand, when the process proceeds from S2 to S4, the three-way valve 36 is driven to open toward the bypass path 9b, and this control routine is returned.
On the other hand, when the process proceeds from S2 to S5, the three-way valve 36 is driven to open toward the second regenerator 34, and the present control routine is returned.

このように、ＥＣＵ４４にて三方弁開度制御が開始されると、上記一連の制御ルーチンが繰り返し実行される。
以上のように、本実施形態では、ＲＣ回路８が膨張機２０出口の冷媒にて蒸発器１０入口、蒸発器１０出口の冷媒をそれぞれ加熱する第１、第２再生器３２，３４を有することにより、凝縮器の熱負荷は不変のままで、膨張機２０入口における冷媒の加熱量、ひいてはＲＣ回路８における回収エネルギーを増大することができるため、廃熱利用装置２のエネルギー回収効率を向上することができる。 As described above, when the ECU 44 starts the three-way valve opening degree control, the series of control routines are repeatedly executed.
As described above, in the present embodiment, the RC circuit 8 includes the first and second regenerators 32 and 34 that heat the refrigerant at the evaporator 10 outlet and the refrigerant at the evaporator 10 outlet with the refrigerant at the outlet of the expander 20, respectively. As a result, the heat load of the condenser remains unchanged and the amount of heat of the refrigerant at the inlet of the expander 20 and thus the recovered energy in the RC circuit 8 can be increased, so that the energy recovery efficiency of the waste heat utilization device 2 is improved. be able to.

また、上記三方弁開度制御を行うことにより、膨張機２０を経由した冷媒を第２再生器３４のバイパス路９ｂと第２再生器３４とに配分して流入させ、エンジン４やＲＣ回路８の作動状況に応じて膨張機２０入口における冷媒の加熱量を適正に制御することができるため、廃熱利用装置２のエネルギー回収効率を更に効果的に向上することができる。
特に、当該三方弁開度制御では、Ｓ１にてＴ２＞Ｔ３が成立しない、Ｔ２≦Ｔ３が成立するとき、Ｓ３にて三方弁３６をバイパス路９ｂ側に強制的に全開させることにより、エンジン４のアイドリング時などにその廃熱が少なくなって蒸発器１０出口の冷媒で膨張機２０出口の冷媒を加熱するといった熱交換の逆転現象を防止することができる。従って、膨張機２０入口における冷媒の温度低下や凝縮を確実に防止できるため、ＲＣ回路８を適正に稼働しつつ、廃熱利用装置２のエネルギー回収効率を確実に向上することができる。 Further, by performing the above three-way valve opening control, the refrigerant having passed through the expander 20 is distributed and introduced into the bypass path 9b of the second regenerator 34 and the second regenerator 34, and the engine 4 or the RC circuit 8 is supplied. Since the amount of heating of the refrigerant at the inlet of the expander 20 can be appropriately controlled according to the operating state of the first, the energy recovery efficiency of the waste heat utilization device 2 can be further effectively improved.
In particular, in the three-way valve opening control, when T2> T3 is not established at S1, and when T2 ≦ T3 is established, the engine 4 is forcibly opened to the bypass path 9b side at S3. When the engine is idling or the like, the waste heat is reduced and the refrigerant at the outlet of the evaporator 10 is heated by the refrigerant at the outlet of the evaporator 10 to prevent the reverse phenomenon of heat exchange. Therefore, since the temperature drop and condensation of the refrigerant at the inlet of the expander 20 can be reliably prevented, the energy recovery efficiency of the waste heat utilization device 2 can be reliably improved while the RC circuit 8 is operating properly.

更に、当該三方弁開度制御では、Ｔ１＞１５０℃が成立するとき、三方弁３６をバイパス路９ｂ側に開駆動させ、一方、Ｔ１＞１５０℃が成立しない、すなわちＴ１≦１５０℃が成立するとき、三方弁３６を第２再生器３４側に開駆動させることにより、冷媒の加熱量の増大に伴い冷媒の温度が極端に高温になることを防止できる。
具体的には、Ｔ１の大きさを冷媒やこの冷媒に添加される潤滑油の劣化・分解を確実に防止できる温度である１５０℃で判定することにより、冷媒温度を冷媒、及び冷媒に添加される潤滑油の分解・劣化を防止可能な最大値とすることができるため、ＲＣ回路８を適正に稼働させつつ、廃熱利用装置２のエネルギー回収効率を更に確実に向上することができる。 Further, in the three-way valve opening control, when T1> 150 ° C. is established, the three-way valve 36 is driven to open toward the bypass passage 9b, while T1> 150 ° C. is not established, that is, T1 ≦ 150 ° C. is established. When the three-way valve 36 is driven to open toward the second regenerator 34, the temperature of the refrigerant can be prevented from becoming extremely high as the heating amount of the refrigerant increases.
Specifically, the refrigerant temperature is added to the refrigerant and the refrigerant by determining the size of T1 at 150 ° C., which is a temperature that can reliably prevent deterioration and decomposition of the refrigerant and the lubricating oil added to the refrigerant. Therefore, the energy recovery efficiency of the waste heat utilization apparatus 2 can be improved more reliably while the RC circuit 8 is properly operated.

また、加熱器１８を有することにより、膨張機２０入口の冷媒の加熱量、ひいてはＲＣ回路８における回収エネルギーを更に増大することができ、廃熱利用装置２のエネルギー回収効率をより一層向上することができる。
更に、当該三方弁開度制御の操作端としてリニア駆動が可能な三方弁３６を用いることにより、膨張機２０を経由した冷媒を冷媒の全流量域に亘って第２再生器３４とバイパス路９ｂとにリニアに配分して流入させることができるため、三方弁開度制御の制御性が向上し、ＲＣ回路８を適正に稼働しつつ、廃熱利用装置２のエネルギー回収効率をより一層確実に向上することができる。 Moreover, by having the heater 18, the heating amount of the refrigerant at the inlet of the expander 20, and thus the recovered energy in the RC circuit 8, can be further increased, and the energy recovery efficiency of the waste heat utilization device 2 can be further improved. Can do.
Further, by using the three-way valve 36 that can be linearly driven as the operation end of the three-way valve opening control, the refrigerant that has passed through the expander 20 is allowed to flow through the second regenerator 34 and the bypass 9b over the entire flow rate range of the refrigerant. Therefore, the controllability of the three-way valve opening control is improved, and the energy recovery efficiency of the waste heat utilization device 2 is further ensured while the RC circuit 8 is properly operated. Can be improved.

以上で本発明の実施形態についての説明を終えるが、本発明は上記各実施形態に限定されるものではなく、本発明の趣旨を逸脱しない範囲で種々の変更ができるものである。
例えば、上記実施形態では、ＲＣ回路８にＲ１３４ａ冷媒が使用されているが、これに限らず、環境負荷がより小さいＲ１５２ａ冷媒を用いても上記と同様の効果を得ることができる。 Although the description of the embodiment of the present invention has been completed above, the present invention is not limited to the above-described embodiments, and various modifications can be made without departing from the spirit of the present invention.
For example, although the R134a refrigerant is used in the RC circuit 8 in the above embodiment, the present invention is not limited to this, and the same effect as described above can be obtained even if an R152a refrigerant with a smaller environmental load is used.

本発明の一実施形態に係る内燃機関の廃熱利用装置を示した模式図である。It is the schematic diagram which showed the waste heat utilization apparatus of the internal combustion engine which concerns on one Embodiment of this invention. 図１のランキンサイクルの熱収支を示したモリエル線図である。It is the Mollier diagram which showed the heat balance of the Rankine cycle of FIG. 図１のＥＣＵで実行される三方弁開度制御の制御ルーチンを示したフローチャートである。3 is a flowchart showing a control routine of three-way valve opening degree control executed by the ECU of FIG. 1.

符号の説明Explanation of symbols

２ 廃熱利用装置
４ エンジン（内燃機関）
８ ランキンサイクル回路（ランキンサイクル）
９ｂ バイパス路
１０ 蒸発器
１８ 加熱器
２０ 膨張機
２２ 凝縮器
３２ 第１再生器
３４ 第２再生器
３６ リニア三方弁（操作端）
３８ 第１温度検出手段（第１温度センサ）
４０ 第２温度検出手段（第２温度センサ）
４２ 第３温度検出手段（第３温度センサ） 2 Waste heat utilization device 4 Engine (internal combustion engine)
8 Rankine cycle circuit (Rankine cycle)
9b Bypass path 10 Evaporator 18 Heater 20 Expander 22 Condenser 32 First regenerator 34 Second regenerator 36 Linear three-way valve (operating end)
38 1st temperature detection means (1st temperature sensor)
40 Second temperature detection means (second temperature sensor)
42 3rd temperature detection means (3rd temperature sensor)

Claims (8)

内燃機関の廃熱により作動流体を加熱する蒸発器、該蒸発器から流出された作動流体を膨張させて駆動力を発生する膨張機、該膨張機から流出された作動流体を凝縮させる凝縮器を有し、該凝縮器から流出された作動流体が前記蒸発器に流入されて循環するランキンサイクルを備え、
前記ランキンサイクルは、前記膨張機から流出された作動流体にて前記蒸発器に流入される作動流体を加熱する第１再生器と、前記膨張機から流出された作動流体にて前記蒸発器から流出された作動流体を加熱する第２再生器とを有することを特徴とする内燃機関の廃熱利用装置。 An evaporator that heats a working fluid by waste heat of an internal combustion engine, an expander that expands the working fluid that has flowed out of the evaporator to generate a driving force, and a condenser that condenses the working fluid that has flowed out of the expander Comprising a Rankine cycle in which the working fluid discharged from the condenser flows into the evaporator and circulates;
The Rankine cycle includes a first regenerator that heats the working fluid that flows into the evaporator with the working fluid that flows out of the expander, and an outflow from the evaporator that uses the working fluid that flows out of the expander. And a second regenerator for heating the generated working fluid. 前記ランキンサイクルは、前記第２再生器をバイパスするバイパス路と、前記膨張機から流出された作動流体を前記バイパス路と前記第２再生器とに配分して流入させる流量配分制御手段とを有することを特徴とする請求項１に記載の内燃機関の廃熱利用装置。   The Rankine cycle includes a bypass passage that bypasses the second regenerator, and a flow rate distribution control unit that distributes and flows the working fluid discharged from the expander to the bypass passage and the second regenerator. The waste heat utilization apparatus for an internal combustion engine according to claim 1. 前記流量配分制御手段は、前記膨張機に流入される作動流体の温度を検出する第１温度検出手段と、前記膨張機から前記第２再生器に流入される作動流体の温度を検出する第２温度検出手段と、前記蒸発器から前記第２再生器に流入される作動流体の温度を検出する第３温度検出手段と、前記第１〜前記第３温度検出手段にて検出された作動流体の温度に基づいて、前記第２再生器側または前記バイパス路側を連通させるべく開駆動される操作端とからなることを特徴とする請求項２に記載の内燃機関の廃熱利用装置。   The flow rate distribution control means detects the temperature of the working fluid flowing into the expander, and detects the temperature of the working fluid flowing from the expander into the second regenerator. Temperature detecting means; third temperature detecting means for detecting the temperature of the working fluid flowing from the evaporator into the second regenerator; and the working fluid detected by the first to third temperature detecting means. The waste heat utilization apparatus for an internal combustion engine according to claim 2, further comprising an operation end that is driven to open the second regenerator side or the bypass path side based on temperature. 前記流量配分制御手段は、前記第２温度検出手段にて検出された作動流体の温度が前記第３温度検出手段にて検出された温度以下となるとき、前記操作端を前記バイパス路側に全開させることを特徴とする請求項３に記載の内燃機関の廃熱利用装置。   When the temperature of the working fluid detected by the second temperature detecting means is equal to or lower than the temperature detected by the third temperature detecting means, the flow rate distribution control means fully opens the operation end to the bypass path side. The waste heat utilization apparatus for an internal combustion engine according to claim 3. 前記流量配分制御手段は、前記第１温度検出手段にて検出された作動流体の温度が所定の設定温度より大きくなるとき、前記操作端を前記バイパス路側に開駆動させ、前記第１温度検出手段にて検出された作動流体の温度が所定の設定温度以下となるとき、前記操作端を前記第２再生器側に開駆動させることを特徴とする請求項４に記載の内燃機関の廃熱利用装置。   When the temperature of the working fluid detected by the first temperature detection unit is higher than a predetermined set temperature, the flow rate distribution control unit opens the operation end to the bypass path side, and the first temperature detection unit The waste heat utilization of the internal combustion engine according to claim 4, wherein when the temperature of the working fluid detected in step is equal to or lower than a predetermined set temperature, the operation end is driven to open to the second regenerator side. apparatus. 前記所定の設定温度は、前記作動流体の分解温度未満の最大値をなすことを特徴とする請求項５に記載の内燃機関の廃熱利用装置。   The waste heat utilization apparatus for an internal combustion engine according to claim 5, wherein the predetermined set temperature has a maximum value lower than a decomposition temperature of the working fluid. 前記ランキンサイクルは、前記蒸発器を経て前記第２再生器から流出された作動流体を前記内燃機関の排ガスにて加熱する加熱器を有することを特徴とする請求項１乃至６の何れかに記載の内燃機関の廃熱利用装置。   The Rankine cycle has a heater that heats the working fluid that has flowed out of the second regenerator through the evaporator with the exhaust gas of the internal combustion engine. Waste heat utilization device for internal combustion engine. 前記操作端は、前記第１〜前記第３温度検出手段にて検出された作動流体の温度に応じて該操作端の作動位置が連続的に可変駆動されるリニア三方弁であることを特徴とする請求項３乃至７の何れかに記載の内燃機関の廃熱利用装置。   The operating end is a linear three-way valve in which the operating position of the operating end is continuously variably driven according to the temperature of the working fluid detected by the first to third temperature detecting means. The waste heat utilization apparatus for an internal combustion engine according to any one of claims 3 to 7.
JP2007310501A 2007-11-30 2007-11-30 Waste heat utilization device for internal combustion engine Pending JP2009133266A (en)

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Cited By (7)

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JP2011196316A (en) * 2010-03-23 2011-10-06 Toyota Industries Corp Rankine cycle device
CN102588053A (en) * 2011-01-06 2012-07-18 康明斯知识产权有限公司 Rankine cycle wasteheat recovery system
CN102691555A (en) * 2012-04-12 2012-09-26 北京工业大学 Recovery system with heat accumulator for internal combustion engine exhausting waste heat and control method
CN102787944A (en) * 2011-05-18 2012-11-21 J·埃贝斯佩歇合资公司 Exhaust heat utilisation device
JP2014034961A (en) * 2012-08-10 2014-02-24 Hino Motors Ltd Rankine cycle system
JP2014037774A (en) * 2012-08-10 2014-02-27 Hino Motors Ltd Rankine cycle system
WO2014087642A1 (en) * 2012-12-06 2014-06-12 パナソニック株式会社 Rankine cycle device, cogeneration system, and rankine cycle device operation method

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2011196316A (en) * 2010-03-23 2011-10-06 Toyota Industries Corp Rankine cycle device
CN102588053A (en) * 2011-01-06 2012-07-18 康明斯知识产权有限公司 Rankine cycle wasteheat recovery system
US8800285B2 (en) 2011-01-06 2014-08-12 Cummins Intellectual Property, Inc. Rankine cycle waste heat recovery system
US9334760B2 (en) 2011-01-06 2016-05-10 Cummins Intellectual Property, Inc. Rankine cycle waste heat recovery system
CN102787944A (en) * 2011-05-18 2012-11-21 J·埃贝斯佩歇合资公司 Exhaust heat utilisation device
CN102787944B (en) * 2011-05-18 2015-07-01 埃贝斯佩歇废气技术合资公司 Exhaust heat utilisation device
CN102691555A (en) * 2012-04-12 2012-09-26 北京工业大学 Recovery system with heat accumulator for internal combustion engine exhausting waste heat and control method
JP2014034961A (en) * 2012-08-10 2014-02-24 Hino Motors Ltd Rankine cycle system
JP2014037774A (en) * 2012-08-10 2014-02-27 Hino Motors Ltd Rankine cycle system
WO2014087642A1 (en) * 2012-12-06 2014-06-12 パナソニック株式会社 Rankine cycle device, cogeneration system, and rankine cycle device operation method
JPWO2014087642A1 (en) * 2012-12-06 2017-01-05 パナソニックＩｐマネジメント株式会社 Rankine cycle apparatus, combined heat and power system, and operation method of Rankine cycle apparatus
US10364708B2 (en) 2012-12-06 2019-07-30 Panasonic Intellectual Property Management Co., Ltd. Rankine cycle apparatus, combined heat and power system, and rankine cycle apparatus operation method

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